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US7614861B2 - Rotary fluid-driven motor with sealing elements - Google Patents

Rotary fluid-driven motor with sealing elements Download PDF

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Publication number
US7614861B2
US7614861B2 US10/549,677 US54967705A US7614861B2 US 7614861 B2 US7614861 B2 US 7614861B2 US 54967705 A US54967705 A US 54967705A US 7614861 B2 US7614861 B2 US 7614861B2
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motor
seal
casing
rotor
rotor assembly
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US20070041859A1 (en
Inventor
Ehud Nagler
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Hmi Ltd
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Hydro Industries Tynat Ltd
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Assigned to HYDRO-INDUSTRIES TYNAT LTD. reassignment HYDRO-INDUSTRIES TYNAT LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NAGLER, EHUD
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Assigned to HMI LTD. reassignment HMI LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HYDRO-INDUSTRIES TYNAT LTD.
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/123—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with tooth-like elements, extending generally radially from the rotor body cooperating with recesses in the other rotor, e.g. one tooth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/18—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/10—Sealings for working fluids between radially and axially movable parts

Definitions

  • the present invention relates to rotary fluid-driven motors and, in particular, it concerns rotary water-driven or air-driven motors which employ sealing elements.
  • Rotary hydraulic motors are motors which are driven by static fluid pressure. In other words, they are designed geometrically such that the balance of surfaces acted upon by the inlet liquid pressure is always eccentric to the axis of rotation. The product of the balance of surfaces and the liquid pressure together with the eccentricity (the perpendicular distance of the balance of surfaces from the axis of rotation) generates a net moment in the direction of rotation.
  • Known types of hydraulic motor operating according to these principles include various types of vane motors and gear motors. Motors of these types tend to suffer from internal leakage from the high-pressure inlet region to the low-pressure outlet region. Leaks of this kind do not perform “work”, i.e., they do not contribute to positive displacement of the parts of the motor, and they therefore reduce power efficiency of the motor. Accordingly, such leaks need to be minimized by internal sealing mechanisms within the motor.
  • Turbine-type motors As an alternative to static-fluid-pressure driven motors, many existing water-driven devices employ turbine-type motors where a rotor is driven by kinetic energy transferred from a flow of water impinging upon the rotor blades. Such a device is necessarily not sealed, and therefore does not require high precision manufacturing techniques. Turbine-type devices, however, offer very low efficiency and are particularly problematic at low flow rates.
  • the present invention is a first invention.
  • a static-fluid-pressure-driven rotary motor for converting fluid pressure at an inlet into a mechanical rotary output
  • the motor comprising: (a) a casing defining a chamber having a fluid inlet and a fluid outlet; and (b) at least one rotor assembly rotatably mounted within the casing, the rotor assembly including: (i) a rotor mounted so as to be rotatable about an axis of rotation; (ii) a plurality of barrier elements associated with, and extending outwards from, the rotor, each of the barrier elements having an outer edge configured for passing in proximity to a facing wall of the casing chamber; and (iii) a resilient seal associated with at least the outer edge of each of the barrier elements, the resilient seal being configured to form a sliding seal between the outer edge and the facing wall while accommodating variations in clearance between the outer edge and the facing wall.
  • the motor of the present invention is implemented as a gear motor, wherein the at least one rotor assembly is implemented as a pair of the rotor assemblies, and wherein the barrier elements are implemented as gear teeth, the pair of rotor assemblies being mounted with the axes of rotation parallel such that the gear teeth intermesh.
  • the motor of the present invention is implemented as a vane motor, wherein the at least one rotor assembly is mounted with the axis of rotation eccentrically located with respect to the casing, and wherein each of the barrier elements is implemented as a vane radially displaceable relative to the axis of rotation.
  • the vanes are radially displaceable within slots formed in the rotor, the rotor assembly further including at least one resilient vane-slot seal deployed to form a sliding seal between each of the vanes and facing surfaces of a corresponding one of the slots.
  • the casing is formed with a guide track and wherein each of the vanes is provided with track-engaging features for engagement with the guide track, the guide track being deployed so as to maintain a predefined spacing between each of the vanes and the facing wall of the housing during rotation of the rotor assembly.
  • the guide track is implemented as a channel formed in an axial end wall of the casing, and wherein the track-engaging features are implemented as a slider block projecting axially from each of the vanes for sliding engagement within the guide channel.
  • the resilient seal includes an elastomeric seal element deployed so as to contact the facing wall of the housing during operation of the motor.
  • each of the barrier elements includes an outward facing slot, and wherein each of the elastomeric seal elements is deployed at least partially within a corresponding one of the outward facing slots.
  • the elastomeric seal element is formed with a substantially circular cross-sectional shape.
  • the elastomeric seal element is formed with a pair of diverging tapered blades for sliding against the facing wall of the casing.
  • the resilient seal is a pressure-responsive seal configured such that a fluid pressure differential applied between opposite sides of the barrier enhances a sealing effect of the seal.
  • the resilient seal includes a substantially rigid contact element deployed so as to contact the facing wall of the housing during operation of the motor, the substantially rigid contact element being resiliently mounted relative to the corresponding one of the barrier elements.
  • the contact element is supported by a spring deployed so as to bias the contact element towards the facing wall of the casing.
  • the contact element is supported by elastomeric material deployed so as to bias the contact element towards the facing wall of the casing.
  • the contact element is integrally formed with the barrier element, the contact element being interconnected with the barrier element through an integral hinge.
  • each of the barrier elements has upper and lower edges
  • the rotor assembly further includes upper and lower seal elements associated with the upper and lower edges and forming a sliding seal between the barrier elements and upper and lower surfaces, respectively, of the chamber.
  • the upper and lower seal elements are contiguous with the resilient seals.
  • the upper and lower seal elements extend substantially radially relative to the axis of rotation.
  • the rotor assembly further includes a rotor seal arrangement substantially circumscribing the axis of rotation and deployed for sealing between ends of the rotor and upper and lower surfaces of the chamber.
  • a floating seal plate overlying an end of the rotor assembly and biased against the rotor assembly by at least one biasing arrangement such that the floating seal plate seals against the rotor assembly.
  • a connector configuration associated with the fluid inlet of the motor and adapted for interconnection with a standard domestic water supply connector.
  • the casing is formed primarily from plastic material.
  • FIG. 1 is a graph showing the volumetric efficiency of conventional rotary hydraulic motors as a function of flow rate.
  • FIG. 2 is a graph showing the volumetric efficiency of a rotary hydraulic motor, constructed and operative according to the teachings of the present invention, as a function of flow rate.
  • FIG. 3A is a partially transparent isometric view of a vane motor, constructed and operative according to the teachings of the present invention
  • FIG. 3B is an isometric view of the vane motor of FIG. 3A with a cover portion of a casing removed;
  • FIG. 3C is an exploded isometric view of the vane motor of FIG. 3A ;
  • FIG. 3D is an isometric view of a vane element from the vane motor of FIG. 3A ;
  • FIG. 4A is a partially transparent isometric view of a first variant implementation of a vane motor, constructed and operative according to the teachings of the present invention
  • FIG. 4B is an isometric view of the vane motor of FIG. 4A with a cover portion of a casing removed;
  • FIG. 4C is an exploded isometric view of the vane motor of FIG. 4A ;
  • FIG. 4D is an isometric view of a rotor from the vane motor of FIG. 4A with the vanes removed;
  • FIG. 5A is a partially transparent isometric view of a second variant implementation of a vane motor, constructed and operative according to the teachings of the present invention
  • FIG. 5B is an isometric view of the vane motor of FIG. 5A with a cover portion of a casing removed;
  • FIG. 5C is an exploded isometric view of the vane motor of FIG. 5A ;
  • FIG. 5D is an isometric view of a rotor assembly from the vane motor of FIG. 5A ;
  • FIG. 5E is a schematic isometric view showing the engagement of a single vane within a guide channel formed in a casing of the vane motor of FIG. 5A ;
  • FIG. 6A is a partially transparent isometric view of a gear motor, constructed and operative according to the teachings of the present invention.
  • FIG. 6B is an isometric view of the gear motor of FIG. 6A with a cover portion of a casing removed;
  • FIG. 6C is an exploded isometric view of the gear motor of FIG. 6A ;
  • FIG. 6D is an isometric view of a rotor assembly (in this case, a gear) from the gear motor of FIG. 6A ;
  • FIGS. 7-11 are schematic transverse cross-sectional views illustrating various preferred implementations of a resilient seal constructed and operative according to the teachings of the present invention, for use in the rotary motors of FIGS. 3A-6D ;
  • FIG. 12 is a schematic axial cross-sectional view illustrating an alternative preferred implementation for axial sealing of the rotary motors of FIGS. 3A-6D .
  • the present invention is a rotary water-pressure-driven or air-pressure-driven motor with supplementary sealing elements.
  • the present invention addresses the aforementioned problems of implementing rotary water-driven or air-driven motors using injection-molded plastic components and/or driven by relatively low input fluid pressures such as less than 10 atmospheres where the manufacturing tolerances between the moving elements and the motor casing are accommodated by resilient seals.
  • the seals are contact seals (as opposed to the non-contact clearance seals of most hydraulic motors) and may be implemented using various elastomeric seals, rigid seals with resilient biasing elements, or combinations thereof.
  • the use of resilient sealing elements makes it possible to use the principles of rotary hydraulic motors without requiring high precision manufacture of the components since the sealing elements themselves accommodate the range of clearances between components.
  • the present invention employs a “positive seal” or “pressure responsive seal”, terms used herein to refer to a seal where application of a pressure differential across the seal acts to enhance the effectiveness of the seal.
  • contact sealing elements in a rotary hydraulic motor also leads to a fundamental change in the volumetric efficiency of the motor such that the asymptotic graph of FIG. 1 changes to approximate to a step function as shown in FIG. 2 . This is because, in contrast to the clearance seals of the prior art, the contact seals of the present invention provide effective leak resistance even at very low flow rates.
  • the present invention provides a static-fluid-pressure-driven rotary motor for converting fluid pressure at an inlet into a mechanical rotary output.
  • the motor includes a casing, which defines a chamber having a fluid inlet and a fluid outlet, and at least one rotor assembly rotatably mounted within the casing.
  • the rotor assembly includes a rotor, a plurality of barrier elements associated with, and extending outwards from, the rotor, and a resilient seal associated with at least an outer edge of each of the barrier elements.
  • the outer edges of the barrier elements passing in proximity to a facing wall of the casing chamber against which the resilient seals for a sliding seal while accommodating variations in clearance between the outer edge of the barrier element and the facing wall of the casing.
  • a first embodiment is a vane motor, wherein the at least one rotor assembly 10 is mounted with the axis of rotation eccentrically located with respect to the casing 12 , 12 ′, and wherein each of the barrier elements is implemented as a vane 14 radially displaceable relative to the axis of rotation.
  • a second embodiment described with reference to FIGS.
  • each barrier element is provided with a resilient seal 24 which forms a sliding seal between the barrier element and the complementary facing wall of the chamber of the casing 12 or 20 .
  • FIGS. 3A-3D these illustrate a first implementation of the vane motor embodiment of the present invention.
  • the motor includes a rotor 10 mounted eccentrically within a motor casing 12 , 12 ′, and a plurality of independent vanes 14 mounted on the rotor so as to be radially displaceable so as to fill the variable spacing between the rotor and the casing wall.
  • resilient seals 24 are provided between the vanes and the motor casing.
  • the rotor assembly further includes at least one resilient vane-slot seal 26 deployed to form a sliding seal between each of vanes 14 and facing surfaces of corresponding vane-receiving slots 28 in the rotor.
  • vane-slot seal 26 A preferred implementation of vane-slot seal 26 as a sealing strip extending along both faces of vane 14 is illustrated in FIG. 3D .
  • Vanes 14 are preferably also provided with upper and lower seal elements 30 extending along the axial ends (upper and lower edges) of the vane substantially radially relative to the axis of rotation. These upper and lower seal elements 30 may advantageously be implemented contiguously as an extension of seals 24 around the ends of the vane.
  • each seal 24 , 26 , 30 may be implemented as a sealing bead or strip deployed within a corresponding slot formed in the rotor or barrier element.
  • bead and slot structures, and alternative seal structures will be discussed below with reference to FIGS. 7-11 .
  • FIGS. 4A-4D show a first variant of the vane motor of FIGS. 3A-3D in which additional sealing elements 32 form a rotor seal arrangement substantially circumscribing the axis of rotation and deployed for sealing between ends of the rotor and upper and lower surfaces of the chamber. This rotor seal arrangement further enhances sealing of the motor against leakage.
  • FIGS. 5A-5E show a second variant of the vane motor of FIGS. 3A-3D in which the radial path of the vanes is guided by a track arrangement.
  • casing 12 , 12 ′ is formed with a guide track (typically either a channel or a ridge) and each vane 14 is provided with track-engaging features for engagement with the guide track.
  • the deployment of the guide track within the casing is arranged so as to maintain a predefined spacing between each of the vanes and the facing wall of the housing during rotation of the rotor assembly.
  • the guide track is implemented as a channel 34 formed in at least one, and preferably both, axial end walls of casing 12 , 12 ′, and the track-engaging features are implemented as a slider block 36 projecting axially from each of vanes 14 for sliding engagement within each guide channel 34 .
  • Each slider block is preferably made from low-friction abrasion-resistant plastic rotatably mounted on a pin projecting axially from the vane. This provides optimal mechanical properties while allowing the main body of the vane to be made from low cost plastics without special properties.
  • the track arrangement ensures that seals 24 function within a predetermined range of clearance and without excessive contact pressure.
  • FIGS. 6A-6D illustrate a second embodiment of the present invention in the form of a gear motor in which two meshed gear wheels rotate within a motor casing.
  • Seals between the meshed gear teeth are typically achieved in the conventional manner by direct contact between surfaces of the teeth as they turn in engagement whereas seals between the extremities of the gear teeth and the surrounding casing, as well as at the axial extremities of the gear wheels, are preferably provided according to the teachings of the present invention by resilient sealing elements.
  • the device includes resilient seals 24 , and preferably also upper and lower seal elements 30 extending substantially radially, and a rotor seal arrangement 32 in this case completely encircling the axis of rotation.
  • the barrier elements are in this case gear teeth 22 which are typically integrally formed with the rotor.
  • the sealing elements may be formed from elastomeric materials or from relatively rigid materials such as various types of plastics, or from any combination of such materials.
  • the resilient seal includes a substantially rigid contact element 50 deployed so as to contact the facing wall of the housing during operation of the motor.
  • substantially rigid is used to refer to any contact element which does not undergo significant deformation during normal operation of the motor.
  • the substantially rigid contact element is resiliently mounted relative to the corresponding one of the barrier elements.
  • the resilient mounting of the contact element may be achieved by mounting the contact element via elastomeric material 52 which functions as a spring deployed so as to bias the contact element towards the facing wall of the casing, as illustrated in FIG. 7 .
  • elastomeric material 52 which functions as a spring deployed so as to bias the contact element towards the facing wall of the casing, as illustrated in FIG. 7 .
  • other types of spring elements may be used.
  • FIG. 11 shows a case where the contact element 50 is integrally formed with the barrier element (vane 14 or gear tooth 22 ), and is interconnected therewith through an integral hinge 54 .
  • the resilient properties of the seal are achieved through flexing of integral hinge 54 .
  • a pressure-responsive sealing configuration is achieved whereby a pressure differential applied between the two sides of the barrier element causes flexing of the hinge and hence brings a sealing edge 56 of the contact element into contact with the casing wall, as shown on the left side of FIG. 11 .
  • the integral hinge returns contact element 50 to its center position as shown on the right side of the figure, slightly spaced from the casing wall.
  • the resilient properties of this structure allow the seal to accommodate significant manufacturing tolerances.
  • Both the cases of FIGS. 7 and 11 provide sufficient resilience to accommodate a range of manufacturing tolerances in the assembly while ensuring that the actual sealing contact surfaces are provided by relatively low-friction and hard-wearing plastic surfaces. These options are therefore believed to be of particular advantage for their wear resistance and reliability.
  • Alternative preferred implementations of the seals of the present invention employ an elastomeric seal element deployed so as to directly contact the facing wall of the housing during operation of the motor. Examples of such implementations are illustrated herein in FIGS. 8-10 .
  • a particularly simple and effective structure for mounting such elastomeric seal elements on the barrier elements has the elastomeric seal elements at least partially deployed within a corresponding outward facing slot formed in the barrier element.
  • the elastomeric seal elements may also be implemented with various different cross-sectional shapes (compare FIGS. 8 and 9 ) according to the typical operating conditions for which they are intended.
  • the geometrical forms of the sealing elements are preferably chosen to keep surface friction effects to a minimum, both in the high-pressure inlet region and in the low-pressure outlet region.
  • the elastomeric seal element is formed with a substantially circular cross-sectional shape.
  • the elastomeric seal element is formed with a pair of diverging blades for sliding against the facing wall of the casing.
  • the diverging blades may optionally be implemented as shown as part of a unitary seal element of X-shaped cross-section. This diverging blade configuration provides bi-directional pressure-responsive sealing.
  • FIG. 10 A further option for implementing the seals of the present invention is illustrated schematically in FIG. 10 .
  • the sealing bead in this case configured be loose fitting within its slot, and is not significantly pressed against the casing wall.
  • the slot housing the seal element is formed with outwardly sloped facing surfaces so as to form a pressure-responsive seal configuration wherein a pressure differential between the two sides of the barrier element urge the sealing element towards the interface between the outwardly sloped slot surfaces and the casing wall, thereby inducing effective contact sealing between the barrier element and the casing wall.
  • the configuration is preferably symmetrical in order to produce bi-directional pressure-responsive sealing (necessary as the vane approaches the fluid inlet).
  • unidirectional sealing may be sufficient since the seal on the side approaching the inlet is formed primarily by surface contact between the gear teeth.
  • FIG. 12 this illustrates an alternative preferred option for achieving sealing of the axial ends of the rotor assemblies.
  • a floating seal plate 60 overlies an end of the rotor assembly and is biased against the rotor assembly by at least one biasing arrangement such that the floating seal plate seals against the rotor assembly.
  • the biasing of floating seal plate 60 against the rotor assembly may be achieved by resilient elements such as one or more elastomeric O-ring 62 deployed between the plate and the casing wall, or may be provided partially or entirely by routing of input supply fluid pressure to the outer face of the floating seal plate.
  • the resilient seals of the present invention render it feasible to employ components produced to a level of precision which can readily be achieved with standard mass-production techniques such as injection molding of plastics. Accordingly, in most preferred implementations, the casing, and typically also the substantially rigid components of the rotor assemblies, are formed primarily from plastic material.
  • preferred implementations include a connector configuration associated with the fluid inlet of the motor and adapted for interconnection with a standard domestic water supply connector.
  • air-pressure-driven implementations preferably feature a connector configuration with a standard air-line connector.
  • rotary motors of the present invention are particularly suited to domestic/household applications of all types, especially where significant power output is required at low flow rates and/or low rates of revolution.
  • Preferred applications include, but are not limited to, water driven hose reels, water driven toys, water driven fans and water driven rotating brushes, and corresponding compressed-air-driven devices.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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US10/549,677 2004-08-17 2005-08-17 Rotary fluid-driven motor with sealing elements Active 2026-11-08 US7614861B2 (en)

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US60196804P 2004-08-17 2004-08-17
PCT/IL2005/000897 WO2006018848A2 (fr) 2004-08-17 2005-08-17 Moteur entraine par un fluide, rotatif, a elements d'etancheite

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US20110070031A1 (en) * 2009-09-23 2011-03-24 Scott Raymond Frazier System for underwater compressed fluid energy storage and method of deploying same
US20110211916A1 (en) * 2010-03-01 2011-09-01 Scott Raymond Frazier Apparatus for storage vessel deployment and method of making same
US20130202470A1 (en) * 2012-02-08 2013-08-08 Shining Golden Yida Welding & Cutting Machinery Manufacture Ltd. Rotary Vane Air Motor with Improved Vanes and Other Improvements
US8876495B2 (en) 2010-12-29 2014-11-04 Eaton Corporation Case flow augmenting arrangement for cooling variable speed electric motor-pumps
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US9551292B2 (en) 2011-06-28 2017-01-24 Bright Energy Storage Technologies, Llp Semi-isothermal compression engines with separate combustors and expanders, and associated systems and methods
US9557079B2 (en) 2010-07-14 2017-01-31 Bright Energy Storage Technologies, Llp System and method for storing thermal energy
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FR2957984B1 (fr) * 2010-03-24 2016-07-29 Barba Willy Del Compresseur ou pompe rotative a palettes semi spheriques "sans huile" pour comprimer ou pomper les fluides gazeux ou liquides
JP2016109029A (ja) * 2014-12-05 2016-06-20 株式会社デンソー ベーン式ポンプ、及び、それを用いる燃料蒸気漏れ検出装置
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